EP0744009B1 - Mehrstufiges regelventil - Google Patents

Mehrstufiges regelventil Download PDF

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Publication number
EP0744009B1
EP0744009B1 EP95908188A EP95908188A EP0744009B1 EP 0744009 B1 EP0744009 B1 EP 0744009B1 EP 95908188 A EP95908188 A EP 95908188A EP 95908188 A EP95908188 A EP 95908188A EP 0744009 B1 EP0744009 B1 EP 0744009B1
Authority
EP
European Patent Office
Prior art keywords
piston
pressure
pistons
partial
stop
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP95908188A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0744009A1 (de
Inventor
Uwe Lehmann
Bodo Stich
Maik Wilhelm
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Daimler AG
Original Assignee
Daimler Benz AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Daimler Benz AG filed Critical Daimler Benz AG
Publication of EP0744009A1 publication Critical patent/EP0744009A1/de
Application granted granted Critical
Publication of EP0744009B1 publication Critical patent/EP0744009B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
    • F16K17/04—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
    • F16K17/0473—Multiple-way safety valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
    • F16K17/04—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
    • F16K17/04—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
    • F16K17/0446—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded with an obturating member having at least a component of their opening and closing motion not perpendicular to the closing faces
    • F16K17/046—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded with an obturating member having at least a component of their opening and closing motion not perpendicular to the closing faces the valve being of the gate valve type or the sliding valve type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
    • F16K17/04—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
    • F16K17/06—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded with special arrangements for adjusting the opening pressure
    • F16K17/065—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded with special arrangements for adjusting the opening pressure with differential piston
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/2496—Self-proportioning or correlating systems
    • Y10T137/2559—Self-controlled branched flow systems
    • Y10T137/2574—Bypass or relief controlled by main line fluid condition
    • Y10T137/2605—Pressure responsive
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7781—With separate connected fluid reactor surface
    • Y10T137/7834—Valve seat or external sleeve moves to open valve
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86928—Sequentially progressive opening or closing of plural valves

Definitions

  • the present invention relates to a multi-stage control valve with a cylinder and a therein actuated piston, which can be acted upon from one side by a regulating pressure and from the other side by the force of a restoring element, e.g. one Compression spring, is applied, the piston depending on the control pressure at least an opening in the wall of the cylinder is not, partially or completely, and so one Flow or pressure connection is interrupted or partially or completely established, and the piston being made up of at least two which can be acted upon with the control pressure
  • a restoring element e.g. one Compression spring
  • Partial piston exists, of which a first partial piston is acted upon by the force of the restoring element.
  • Valves of this type are known from hydraulic control technology.
  • US-A-4,699,171 shows valves that have one inlet and two outlets (or vice versa), the inlet can either be connected to one of the outputs and this connection via Bores or the like is made in the actuating piston, so that optionally depending on Displacement of the control piston either one or the other of the outputs with the input is connected, where appropriate also further displacement positions of the actuating piston can be provided in which, for example, none of the outputs or both with connected to the entrance.
  • the piston is moved by the action of a control pressure on one end of the Piston, while the other end face of a return element, generally one Compression spring, is applied.
  • a control pressure on one end of the Piston
  • the other end face of a return element generally one Compression spring
  • the effective pressure exerted by the regulating pressure is used Piston cross section, the spring constant of the compression spring and the arrangement of the openings and Connection channels selected so that completely in very specific areas of the control pressure certain, desired connections between inputs and outputs are established. It it is understood that such valves in principle have a large number of different inputs and Can have outputs, the connections in the desired pressure range getting produced.
  • the connection for the control pressure can also be used as an input or a of the valve's inputs are used.
  • the object of the present invention is to create a multi-stage control valve with the features mentioned above, which in a wide range a change in the control characteristic depending on the position of the actuating piston even without using multiple reset elements.
  • a driver the sub-pistons together connects that, at least in a certain position range of the partial pistons, too the second partial piston has a restoring force of over the first partial piston and the driver the return element learns that the cylinder has at least one stop for the second Partial piston, which the movement of the second partial piston under the influence of Control pressure and limited against the action of the return element, while the first Partial piston unaffected by this stop with a further increase in pressure against the Reset element remains movable.
  • the driver therefore only acts in one direction, i.e. the second piston is supported the driver only on the first piston and thus experiences the power of Reset element, while the first piston against the force of the reset element also remains movable relative to the second sub-piston when the second piston against one in effective direction has come to bear and the pressure at first Partial piston is sufficient to overcome the restoring force effective in this position.
  • the different partial pistons next to each other can also be arranged in separate cylinders and with each other through the mentioned drivers to connect, an embodiment of the invention is preferred, however which the sub-pistons are concentric with each other as at least one outer and one inner Partial pistons are provided and are telescopically displaceable.
  • the outer partial piston of a reset element e.g. a compression spring is applied and that for the inner Piston provided a stop on a pin extending from a bottom of the cylinder is.
  • a reset element e.g. a compression spring
  • the inner Piston provided a stop on a pin extending from a bottom of the cylinder is.
  • the inner partial piston e.g. by a compression spring is acted upon as a restoring element
  • the wall of the outer piston has a radial opening in the region that can be released by the inner piston
  • the cylinder also has two axially spaced openings, one of which is in the stop position of the outer piston is aligned with the opening in the piston wall while the other during the movement of the outer piston towards the stop from the outer Piston is released.
  • such an embodiment can also easily be more than Expand two pistons, e.g. three relative to each other telescopically and partial pistons connected by a driver can be provided, of which the outer in its wall has two axially spaced openings, while the middle one has such an opening in the two stop positions of the outer and middle Partial piston each with one of the openings of the outer piston and with one of the openings is aligned in the cylinder wall.
  • the cylinder wall then has three openings, one after the other by moving all three pistons, in this case through the top of the outer one Partial piston, and then through the two inner partial pistons, in this case over the edge of the middle part of the piston and through two openings in the outer part piston and the cylinder wall, and finally through the inner part piston, namely through its upper edge and again two more aligned Openings in the cylinder wall and in the outer piston, which also have an opening in the middle part of the piston.
  • a stop can be used expediently step-like tapering of the cylinder inner wall can be provided.
  • Partial piston devices which have a relative rotation of at least the Prevent the outer piston against the cylinder wall to ensure that the respective holes can be aligned with each other.
  • the holes in question can in principle have any cross-sectional shape, in particular also in the longitudinal direction of the pistons and cylinder walls or in their Can be circumferentially extending slots.
  • annular circumferential grooves are provided, even with a relative rotation between the Open the piston and cylinder openings to create a connection between these openings.
  • This concept of ring grooves can be used when using more than two partial pistons also on the guide surfaces of the individual pistons in sliding contact with one another be expanded.
  • Variants of the control valve according to the invention also appear expedient, at which the one or more partial pistons are designed so that after the release of a first opening in the cylinder wall during its movement towards the stop close this opening again with further wall sections, if, or shortly before reach the respective stop position in which an opening in the piston wall with a Another opening in the cylinder wall is aligned.
  • the blind bore 7 in the cylinder 1 is stepped several times in diameter and has in the area of the plug 25 a threaded section with an internal thread 27 on.
  • the diameter region 16 leading the actuating piston 2 is opposite the threaded section 27 somewhat tapered and has a gradation from one at a distance from the floor 8 tapered diameter region 17 even further, this gradation one Stop 6 for the outer piston 22 of the actuating piston 2 forms.
  • blind bore 7 as a through bore form, which is closed by means of a plug.
  • the tapered diameter range 17 and the stop 6 can here by separate part or by corresponding Shaping the plug to be formed.
  • the two-part actuating piston 2 consists essentially of an inner part piston 21 and an outer partial piston 22, which has a driver 5 in the form of a in the inner surface of the Has partial piston 22 recessed spring ring.
  • the outer partial piston 22 is thus a hollow cylindrical part in which the inner piston part 21 is slidably guided.
  • the driver 5 limits the sliding movement of the inner partial piston 21 in the direction of the threaded plug 25.
  • the plug 25 has a bore as a pressure connection for a pressure connection 26, through which the control pressure P is supplied. This control pressure P acts on both annular upper end face 22 'of the outer partial piston 22 and on the circular upper end face 21 'of the inner partial piston 21.
  • the inner partial piston 21 is directly by a compression spring 3 arranged in the blind bore against the direction of directed by the control pressure P on the end face 21 ', 22' of the two partial pistons 21, 22 Preloaded force, this pretensioning force in mechanical equilibrium by the Control pressure on the other side of the piston 21 and, via the driver 5, also on the pressure-side end face of the outer partial piston 22 acting force is compensated.
  • both Partial pistons 21, 22 in engagement with each other to move to their end stop, under the Effect of the control pressure P coming from the outside only moved so far without counterforce until the driver 5 strikes against the end face 21 'of the inner partial piston 21, so that the restoring force of the compression spring 3 not only on the inner piston 21, but also acts on the outer partial piston 22 via the driver 5.
  • the compression spring 3 is there generally dimensioned so that at very low control pressure P or even in the end face 21 ′ of the inner partial piston 21 against the driver 5 is depressurized strikes and the outer partial piston 22 up to the acting as a stop ring formed lower edge 23 'of the plug 25 presses.
  • the upper edge 22 'of the outer partial piston 22 gives the outlet opening 41 in the Wall 11 of the cylinder 1 initially partially and finally completely free, so that the pressure connection 26 and the outlet opening 41 now a continuous connection via the Have print media.
  • the pressure medium can either from the pressure port 26 to Output opening 41 flow or only a static pressure on the effect the outlet opening 41 connecting (not shown) elements.
  • the bore 4 of the partial piston With a further downward movement, the bore 4 of the partial piston finally begins 22 and the second outlet opening 42 in the cylinder wall 11 to overlap and will be in perfect alignment when the lower, annular end face 22 "of the Partial piston 22 reaches the stop 6 formed by the gradation.
  • the Exit openings 41, 42 and the bore 4, the upper and lower end faces 22 ', 22 " of the partial piston 22 and the stop 6 can be arranged largely arbitrarily, so that for example, the overlap of the bore 4 and the outlet openings 42 at the same time the exit opening 41 is released by the upper edge 22 ′ of the partial piston 22, or that this overlap is delayed.
  • the outer partial piston 22 and the corresponding one cylindrical pressure meter area 16 a little longer upwards in the direction of the threaded plug 25 executed and instead of the upper edge of the partial piston 22 as the outlet opening 41 free-floating element is just another hole in the above the driver 5 Wall of the outer sub-piston 22 is provided, which in the downward movement of the outer Partial piston 22 (or both partial pistons 21, 22 together) the connection of the pressure connection 26 with the outlet opening 41, optionally with the interposition of the others Ring groove, manufactures.
  • the exit openings 41 and 42 as well as the additional ones to be attached above the driver 5 (Not shown) hole in the wall 11 of the outer piston 22 optionally one smooth transition can be achieved, in which already in an intermediate pressure range a partial connection between the outlet opening 42 and the pressure connection 26 is established, while also the connection between the outlet opening 41 and the Pressure port 26 still exists, but the arrangement can also be made so that initially the connection between the outlet opening 41 and the pressure connection 26 is prevented is before a connection between the outlet port 42 and the pressure port 26th arises.
  • outlet openings 41, 42 are not on the outer wall of the cylinder 1 must open, but that corresponding connections also at the front, for example on the floor, can also be provided, also connecting nipples or threads can be provided for these connections.
  • Partial piston 32 and thus an additional control stage are an additional one in this case Outlet opening 43 is provided in the cylinder wall 11, thus the outlet openings overall 41, 42, 43.
  • the outer additional partial piston 32 therefore necessarily points two holes 4, 4 'instead of one hole 4 of the embodiment according to FIG.
  • the middle part of the piston 31 has a bore 10.
  • the cylindrical Blind hole 7 of the cylinder 1 is stepped twice to form two stops 6 or 6 'for the outer or middle partial pistons 32, 31.
  • the three partial pistons 30, 31, 32 are also pressurized via connection 26 and initially move together downwards until the upper edge 32 'of the partial piston 32 clears the outlet opening 41 and the partial piston 32 then abuts the stop 6.
  • the bores 4, 4 'of the outer partial piston 32 lie with the outlet openings 42, 43 or with the ring grooves 13 and 14 simultaneously at the same axial height.
  • the middle piston 31 together with the inner piston 30 at a move further pressure rise further downward, so that the upper edge 31 'of the middle part piston 31 finally opens the opening 4, which, as already mentioned, with the Exit opening 42 communicates.
  • Pressure value the connection between the outlet opening 42 and the pressure port 26th produced.
  • the middle piston 31 also reaches the stop 6 ', wherein again the bore 10 is at the same axial height as the bore 4 '. In this Position, the bore 10, 4 'is aligned with the outlet opening 43.
  • the partial pistons 31, 32 can also move upwards over the drivers 5, 5 'also be extended and the function of the edges, which the individual openings release, can again be taken over by appropriate holes in the wall of the partial piston are so that after the release of the individual exit openings 41, 42, 43, the successively from top to bottom, with a corresponding increase in pressure Closing the outlet openings 41, 42, 43 can be effected again if, or before the connection of the pressure connection 26 to the next outlet opening (42 or 43) is produced.
  • Figure 3 shows a further variant, in which a bore in the outer piston 33 can be dispensed with entirely, or the number of holes in one (or the) outer piston 33 can at least be reduced.
  • the first of which serving as the restoring compression spring 3 acted partial piston the outer partial piston 33.
  • the inner partial piston 34 acts only via a driver 5, which is considered to be radially inward protruding collar is formed on the lower edge of the outer piston 33 on the compression spring 3.
  • the pressure connection 26 is in turn provided on a threaded plug 25 and acts on the end faces 33 ', 34' of both partial pistons 33, 34, with the effect of Regulating pressure P both partial pistons 33 which are in engagement with one another via the driver 5, 34 move down together and, as shown in Figure 3, gradually Release the outlet opening 41 and thus establish its connection to the connection 26.
  • the central pin 35 which projects from the bottom 8 of the cylinder 1 into the blind bore 7 and is enclosed by the spring 3, limits the path of the inner piston part 34. In one sufficient pressure increase the inner piston 34 finally reaches the stop of the Pin 35 so that its further downward movement is now stopped and the force for a further compression of the compression spring 3 alone from the annular end face 33 'of the outer partial piston 33 must be applied compressive force. First if through a corresponding pressure increase this effective loss of effective End face of the actuating piston 2 is compensated, the outer piston 33 moves further downwards and can finally also the outlet opening 42 for connection to the Release pressure port 26.
  • FIG. 4 Such a variant is shown in FIG. 4.
  • the outer cylinder wall has two exit openings 41, 42 and the middle partial piston has only one through hole 4.
  • the position and size of the through hole 4, in particular their distance from the upper edge of the piston 33, and by the location and Size of the outlet openings 41 and 42 and the location of the stops can determine whether for example, always only one of the two outlet openings 41, 42 connects to may have the pressure connection or whether both outlet openings in certain pressure conditions 41, 42 can be connected to the pressure connection 26.
  • annular circumferential grooves 12, 13 are provided at the axial height of the outlet openings 41, 42 which, however, are only required when connecting to the exit openings 41, 42 are produced via bores in the wall of the outer partial piston 33 should and if you take special measures to align the partial piston 34 and cylinder 1 wants to avoid in the circumferential direction.
  • Relief bores 36 are provided in the housing of the cylinder 1 on the pressure-facing piston side. Furthermore, the relief bores 36 an additional pressure to support the spring can be applied.
  • FIG. 5 The characteristic of a multi-stage control valve, as described above, is shown in FIG. 5.
  • the system pressure as it prevails in the area of the pressure connection 26 and acts on the end faces of the partial pistons, is plotted in the vertical direction over the adjustment path s of the partial piston which is in engagement with the spring 3 and which is movable the longest.
  • a very low pressure which is assumed to be O in FIG. 5, and without spring preload, all the partial pistons move together, the actuating path being proportional to the force acting on the piston end faces, which is again proportional, according to the spring characteristics to print. This results in the course of a straight line section a starting from the origin in the pressure / displacement path diagram.
  • the second part of the piston does not move further at first, since the force on its end face at the pressure P 1 then prevailing is not sufficient at first, and it counteracts the force of the spring 3 to move on.
  • the pressure can therefore initially rise without any further piston displacement, which is illustrated by the first vertical section b of the graph in FIG. 5.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Fluid-Driven Valves (AREA)
EP95908188A 1994-02-11 1995-02-09 Mehrstufiges regelventil Expired - Lifetime EP0744009B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4404358A DE4404358C2 (de) 1994-02-11 1994-02-11 Eingangsdruckgesteuertes Mehrwegeventil
DE4404358 1994-02-11
PCT/DE1995/000170 WO1995022025A1 (de) 1994-02-11 1995-02-09 Mehrstufiges regelventil

Publications (2)

Publication Number Publication Date
EP0744009A1 EP0744009A1 (de) 1996-11-27
EP0744009B1 true EP0744009B1 (de) 1998-08-12

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP95908188A Expired - Lifetime EP0744009B1 (de) 1994-02-11 1995-02-09 Mehrstufiges regelventil

Country Status (7)

Country Link
US (1) US5704386A (ko)
EP (1) EP0744009B1 (ko)
JP (1) JP2707367B2 (ko)
KR (1) KR0180348B1 (ko)
BR (1) BR9506760A (ko)
DE (2) DE4404358C2 (ko)
WO (1) WO1995022025A1 (ko)

Families Citing this family (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19605247C1 (de) * 1996-02-13 1997-04-24 Siemens Ag Vorrichtung zum Steuern eines Volumenstromes
DE19717922A1 (de) * 1997-04-28 1998-10-29 Schwaebische Huettenwerke Gmbh Zweistufenregelventil
US7429243B2 (en) * 1999-06-03 2008-09-30 Cardiac Intelligence Corporation System and method for transacting an automated patient communications session
DE102006032314A1 (de) * 2006-07-11 2008-02-14 Thyssenkrupp Presta Steertec Gmbh Regelventil für eine Servolenkung
WO2009095011A2 (de) * 2008-01-31 2009-08-06 Dieter Voigt Druckumschaltung für ölpumpen
GB0815761D0 (en) * 2008-09-01 2008-10-08 Rolls Royce Plc Swirler for a fuel injector
US8708376B2 (en) * 2008-10-10 2014-04-29 Deka Products Limited Partnership Medium connector
DE102009053814B4 (de) * 2009-11-18 2013-11-14 Knorr-Bremse Systeme für Schienenfahrzeuge GmbH Mehrstufig schaltbare vorgesteuerte Ventilanordnung
CN103062461A (zh) * 2013-01-28 2013-04-24 苏州宇东暖通技术有限公司 一种可调压力的泄压阀
DE102015221515B4 (de) * 2015-11-03 2022-03-31 Zf Friedrichshafen Ag Ventilanordnung zur Begrenzung von Druckspitzen in einem Hydrauliksystem eines Automatikgetriebes
US10865718B2 (en) 2016-03-07 2020-12-15 Westport Power Inc. Pressure regulating modules with controlled leak paths
CN107893860A (zh) * 2017-12-07 2018-04-10 湖北中瑞天恒节能科技发展有限公司 燃气阀及防回火灶具
DE102018200359A1 (de) * 2018-01-11 2019-07-11 Robert Bosch Gmbh Ventilanordnung zur Gasdruckregelung, Kraftstoffsystem mit Ventilanordnung zur Gasdruckregelung
CN111699320B (zh) * 2018-01-30 2022-06-03 法雷奥日本株式会社 可变容量型压缩机
CN108561480B (zh) * 2018-04-28 2023-09-01 浙江易锻精密机械有限公司 一种上死点缓冲气垫
US10969036B2 (en) * 2018-05-30 2021-04-06 Lam Research Corporation High flow multi-way piston valve for deposition systems
KR102230161B1 (ko) * 2019-03-20 2021-03-22 미노언 주식회사 공기호흡기용 레귤레이터의 제어장치
DE102019212542B4 (de) * 2019-08-22 2022-05-12 Thyssenkrupp Ag Überdruckventil mit Volumenausgleich
CN110645368B (zh) * 2019-10-14 2021-11-12 中国船舶科学研究中心（中国船舶重工集团公司第七0二研究所） 一种深海应急逃生阀
CN111518597B (zh) * 2020-05-06 2021-10-15 长沙宁湖机械设备有限公司 一种用于天然气回收多级控压器
KR102507202B1 (ko) * 2022-08-16 2023-03-07 (주)에스투엠 유류 운반용 탱크로리의 안전밸브

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US423003A (en) * 1890-03-11 Valve
US2173819A (en) * 1938-07-05 1939-09-26 Wagner Electric Corp Compressor shut-off valve
US2507384A (en) * 1946-01-11 1950-05-09 Bendix Aviat Corp Snap-action pilot valve
US2510052A (en) * 1946-01-18 1950-06-06 Navarro Miguel Pressure control device for pneumatic tires
US2724239A (en) * 1952-04-21 1955-11-22 Samuel S Fox Fuel flow distributing and manifold pressurizing valve for dual orifice fuel injection nozzles
US2890715A (en) * 1955-08-26 1959-06-16 Warner Swasey Co Multi-pressure relief valve
US3007481A (en) * 1959-12-30 1961-11-07 Clark Equipment Co Pressure regulator
US3450155A (en) * 1964-02-06 1969-06-17 Us Navy Frictionless relief valve
US3298386A (en) * 1964-06-15 1967-01-17 Rexall Drug Chemical System for establishing a plurality of fluid pressure levels
US3898999A (en) * 1972-11-17 1975-08-12 Jordan D Haller Valve having axially separable members
DE2718168C3 (de) * 1975-10-29 1979-11-29 Wabco Fahrzeugbremsen Gmbh, 3000 Hannover Druckregelventil für eine Doppelachs-Luftfederung von Nutzfahrzeugen
US4478558A (en) * 1980-08-04 1984-10-23 D. W. Zimmerman Mfg., Inc. Downhole pump with check valve
US4699171A (en) * 1986-12-19 1987-10-13 Sundstrand Corporation Multiple port relief valve
DE4224973C2 (de) * 1992-07-29 1995-08-03 Glyco Metall Werke Fluidversorgungssystem mit Druckbegrenzung

Also Published As

Publication number Publication date
DE4404358A1 (de) 1995-08-17
US5704386A (en) 1998-01-06
WO1995022025A1 (de) 1995-08-17
KR960706042A (ko) 1996-11-08
DE59503162D1 (de) 1998-09-17
KR0180348B1 (ko) 1999-04-15
DE4404358C2 (de) 1998-04-09
JP2707367B2 (ja) 1998-01-28
JPH09504596A (ja) 1997-05-06
BR9506760A (pt) 1997-10-07
EP0744009A1 (de) 1996-11-27

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